Power-split continuously variable transmission with two driving ranges

Abstract

Power-split continuously variable transmission (1) with a drive (10), an output (11), a first and a second planetary gear set (2, 3), a variator with a first and a second energy converter (20; 20''', 21; 21'''), and a first and a second switching device (K1, K2; K2'); wherein the planetary gear sets (2, 3) each comprise three elements, the first element of the respective planetary gear set being formed by a sun gear (4, 5), the second element of the respective planetary gear set being formed by a planet carrier (6, 7) in the case of a negative planetary gear set and by a ring gear in the case of a positive planetary gear set, and the third element of the respective planetary gear set being formed by a ring gear (8, 9) in the case of a negative planetary gear set and by a planet carrier in the case of a positive planetary gear set;wherein the second element (7) of the second planetary gear set (3) is permanently rotationally fixed to the third element (8) of the first planetary gear set (2) and mechanically operatively connected to the drive (10), the first energy converter (20; 20''') is mechanically operatively connected to the first element (4) of the first planetary gear set (2) and the second energy converter (21; 21''') is mechanically operatively connected to the second element (6) of the first planetary gear set (2), and the second element (6) of the first planetary gear set (2) can be rotationally fixed to the output (11) via the first switching device (K1) in order to provide a first transmission range (FB1);and wherein the first element (4) of the first planetary gear set (2) is connected to the first element (5) of the second planetary gear set (3) via a first connection and the third element (9) of the second planetary gear set (3) is connected to the output (11) via a second connection, characterized in that the first connection can be switched via the second switching device (K2) to establish a rotationally fixed connection in order to provide the second transmission range (FB2), and the second connection is designed as a permanently rotationally fixed connection.

Description

[0001] The present invention relates to a power-split continuously variable transmission with two driving ranges. The transmission can be configured for use in a machine. Furthermore, the present invention relates to a drive train for a machine with such a power-split continuously variable transmission, and to a machine with such a drive train.

[0002] Power-split continuously variable transmissions (CVTs), such as hydrostatic-mechanical CVTs, are frequently used in machinery. These transmissions allow for stepless adjustment of the gear ratio with relatively high efficiency, but they have a comparatively narrow gear ratio spread. The gear ratio spread of a transmission is the ratio between the highest and lowest gear ratios. It is known to incorporate several operating ranges in a CVT, each with a different gear ratio range, to increase the gear ratio spread.

[0003] The present invention relates to a power-split continuously variable transmission. In a continuously variable transmission, the gear ratio is infinitely variable. The transmission can be designed for use in a machine, for example, a construction or agricultural machine. The power split can be, for example, a hydrostatic-mechanical and / or an electromechanical power split. The transmission comprises an input, to which the quantity to be converted is fed into the transmission. The transmission also comprises an output, to which the quantity converted by the transmission is discharged. Furthermore, the transmission comprises a variator with a first and a second energy converter, which can be coupled to each other and operatively connected. The variator can be a hydraulic and / or electric variator.The variator is designed to allow stepless variation of the transmission's gear ratio. Furthermore, the transmission has a first and a second shifting device. A shifting device can be a clutch. The shifting devices can be designed as positive-locking devices, such as dog clutches and / or synchronizers, and / or as friction-locking devices, such as multi-plate clutches.

[0004] The transmission has a first and a second planetary gear set. The transmission can only have a first and second planetary gear set, and therefore no further planetary gear sets. In one embodiment, the transmission can have only two planetary gear sets in the power flow between the input to the second planetary gear set and the output. Each of the planetary gear sets can be a negative planetary gear set, in which the stationary gear ratio, which describes the speed ratio of the sun gear and ring gear when the carrier is fixed, is negative. Likewise, one or both planetary gear sets can be a positive planetary gear set, in which the stationary gear ratio is positive. It is conceivable that the first planetary gear set is a negative or a positive planetary gear set and the second planetary gear set is a negative planetary gear set.

[0005] Each planetary gear set has three elements. The first element of each planetary gear set is a sun gear. The second element is a planet carrier in the case of a negative planetary gear set and a ring gear in the case of a positive planetary gear set. The third element is a ring gear in the case of a negative planetary gear set and a planet carrier in the case of a positive planetary gear set. The planet carrier is also known as a planet carrier or carrier. In the case of a negative planetary gear set, the planet carrier can support at least one, but more specifically several, for example, three, planet gears, each of which meshes with both the sun gear and the ring gear. In the case of a positive planetary gear set, the planet carrier can support at least one, but more specifically several, for example, three, pairs of planet gears.One of the planet gears of each pair can mesh with the sun gear and the other with the ring gear, with the two planet gears also being able to mesh with each other.

[0006] If two elements are mechanically connected, they are coupled directly or indirectly in such a way that a movement of one element causes a reaction in the other. Further elements, such as one or more gear stages, may be provided between the elements. A permanently non-rotatable connection between two elements is understood to be a connection in which the two elements are rigidly coupled to each other in all intended states of the transmission. The elements may be individual components rigidly connected to each other or even as a single piece. In a permanently non-rotatable connection between two elements, the elements are directly and immediately connected to each other, without any further functional groups, such as transmission stages, being provided between them. Only a connecting element to establish the rigid coupling between the elements may be provided.

[0007] If, however, a switching element is provided between two components of the transmission, these components are not permanently and rotationally fixed to each other, but can be connected to each other via the switching element. A rotationally fixed coupling is only achieved by actuating the intermediate switching element. Actuating the switching element means that it is brought into a closed state, so that the rotational movements of the components directly coupled to the switching element are synchronized. If the switching element in question is designed as a positive-locking switching element, the components directly and rotationally fixed to each other via this element will rotate at the same speed. In the case of a friction-locking switching element, speed differences between the components can exist even after it has been actuated.This desired or unintended state can nevertheless be described as a rotationally fixed connection of the respective components.

[0008] The second element of the second planetary gear set is permanently and rotationally fixed to the third element of the first planetary gear set and mechanically operatively connected to the drive. Furthermore, the first energy converter is mechanically operatively connected to the first element of the first planetary gear set, and the second energy converter is mechanically operatively connected to the second element of the first planetary gear set. The second element of the first planetary gear set can be rotationally fixed to the output via the first switching device in order to provide a first transmission range with a first gear ratio range.

[0009] Furthermore, the first element of the first planetary gear set is connected to the first element of the second planetary gear set via a first connection, and the third element of the second planetary gear set is connected to the output via a second connection. One of the first and second connections can be switched via the second switching device to establish a rotationally fixed connection, thus providing a second gear range with a second transmission ratio. The other of the first and second connections is designed as a permanently rotationally fixed connection. The first and second transmission ratios can differ in order to increase the gear ratio spread. Thus, either the first element of the first planetary gear set can be rotationally fixed to the first element of the second planetary gear set via the second switching device, or the third element of the second planetary gear set can be rotationally fixed to the output via the second switching device.

[0010] The present invention provides a power-split continuously variable transmission with two driving ranges and thus a relatively large gear ratio spread. The transmission has a simple, compact, and cost-effective design because it comprises only two planetary gear sets and only two switching devices. Furthermore, the transmission results in low component and variator loads and exhibits good efficiency.

[0011] In one embodiment, the second element of the first planetary gear set and the output shaft are permanently and rotationally fixed to the first switching device. Furthermore, the first element of the first planetary gear set and the first element of the second planetary gear set can be permanently and rotationally fixed to the second switching device. Alternatively, the third element of the second planetary gear set and the output shaft can be permanently and rotationally fixed to the second switching device.

[0012] The variator's energy converters can be designed as electric machines. Each electric machine can include power electronics. Furthermore, it is conceivable that the electric machines provide electrical power to a consumer, and that electrical power can therefore be drawn from the transmission via the variator. In one embodiment, the electric machines can each be operated as a motor and a generator. It is also conceivable that one of the machines can be operated only as a motor and the other only as a generator. Alternatively or additionally, the energy converters can be designed as hydrostatic drives.

[0013] One or both of the energy converters can be mechanically connected to the first planetary gear set via a pre-reduction stage. This pre-reduction stage can be a spur gear and / or a planetary gear stage. If the energy converters are electric machines, the pre-reduction stage makes it possible, for example, to use smaller electric machines.

[0014] At least one of the energy converters can be designed coaxially with the drive. A coaxial design of the energy converter to the drive means that the rotational axis of the energy converter coincides with the rotational axis of the drive. This allows for a particularly compact and rotationally symmetrical gearbox. This design also enables the energy converter to be connected to the gearbox with fewer components. This results in low complexity and reduced susceptibility to failure.

[0015] Furthermore, it is possible for at least one of the energy converters to be designed axially parallel to the drive. In this configuration, the axis of rotation of the energy converter does not coincide with that of the drive, but is arranged parallel to it. This embodiment has the advantage that the design of the energy converter, for example its size, can be selected independently of the design of the rest of the gearbox. If both energy converters are axially parallel, they can be provided on opposite sides of the gearbox. In an axially parallel configuration, the energy converter can be mechanically connected to the planetary gear set via one or more spur gear stages.

[0016] The transmission can also include a reversing gear. By providing the reversing gear, the first and second transmission ranges can be made available in both forward and reverse directions. The reversing gear can be located on the output side, where it can be mechanically coupled to the transmission output or permanently fixed against rotation. In this case, the reversing gear can be located in the power flow downstream of the transmission output. Likewise, the reversing gear can be located on the input side and in the power flow upstream of the transmission input. For example, the reversing gear can be permanently fixed against rotation to the second element of the second planetary gear set. The reversing gear can include a negative planetary gear set, a positive planetary gear set, and / or a spur gear stage.

[0017] The first and second planetary gear sets can each be designed as negative planetary gear sets. This results in a simple and particularly compact gearbox design. Furthermore, the first and second planetary gear sets can have identical geometric dimensions. For example, the sun gears, planet gears, and ring gears of both planetary gear sets can have identical diameters. This also contributes to a simple and compact gearbox design. The gearbox can also include a power take-off (PTO) shaft, which can be permanently and rotationally fixed to the drive. The PTO shaft can also be referred to as a secondary drive. Drive power can be supplied via the PTO shaft to auxiliary equipment, such as a mower, a forage wagon, or other implements.

[0018] Furthermore, the present invention relates to a drive train for a working machine with a power-split continuously variable transmission according to one of the previously described embodiments. The invention also relates to a working machine with such a drive train. The working machine can be an agricultural machine or a construction machine. For example, the working machine is an agricultural tractor or a wheel loader. Fig. Figure 1 shows a schematic view of a gearbox according to a first embodiment of the present invention. Fig. Figure 2 shows a schematic view of a transmission according to a further embodiment of the present invention. Fig. Figure 3 shows a shift pattern of the transmissions from Fig. 1-2. Fig. Figure 4 shows a schematic view of a transmission according to a further embodiment of the present invention. Fig. Figure 5 shows a schematic view of a transmission according to a further embodiment of the present invention. Fig. Figure 6 shows a schematic view of a transmission according to a further embodiment of the present invention. Fig. Figure 7 shows a schematic view of a transmission according to a further embodiment of the present invention.

[0019] Fig. Figure 1 shows a schematic representation of a gearbox. 1 according to a first embodiment of the present invention. The gearbox 1 The present embodiment is essentially axially symmetrical, wherein in Fig. Figure 1 shows only a schematic half-section. Furthermore, the gearbox is... 1 designed to be integrated into the drive train of a working machine.

[0020] The gearbox 1 includes a first planetary gear set 2and a second planetary gear set 3 Each of the planetary gear sets 2 , 3 indicates a first element 4 or 5 , a second element 6 or 7 , and a third element 8 or 9 up. The first element 4 of the first planetary gear set 2 and the first element 5 of the second planetary gear set 3 Each element is formed by a sun wheel. The second element 6 of the first 2 and the second element 7 of the second planetary gear set 3 Each element is formed by a planetary carrier. The third element 8 of the first 2 and the third element 9 of the second planetary gear set 3 Each is formed by a ring gear. The first and second planetary gear sets 3In this first embodiment, each planetary gear set is designed as a negative planetary gear set. The planet carriers 6 , 7 the planetary gear sets 2 , 3 Each planet gear carries several planetary gears, with in Fig. Only one planet gear is shown in each case. The planet gears mesh with both the sun gear and the sun gear. 4 or 5 as well as the ring gear 8 or 9 of the respective wheelset 2 or 3 .

[0021] The gearbox 1 It also features a drive 10 and a drive 11 on, which are located on opposite sides of the gearbox 1 are planned. The drive 10 In this case, it is formed by a drive shaft that extends from the side of a gearbox input. 13 completely through the gearbox 1 through to the side of a gearbox output 14 extends at which the downforce11 is arranged. On the output side. 11 forms the drive shaft 10 a power take-off or PTO shaft 12 out. Between the gearbox input 13 and the gearbox output 14 are the first and second planetary gear sets 2 , 3 arranged in this order. In the present embodiment, the first and second planetary gear sets are 2 , 3 geometrically essentially identical to each other and coaxial to the drive shaft 10 trained. Thus, the sun wheels indicate 4 or 5 , the planetary carriers 6 or 7 , and the hollow gears 8 or 9 the two planetary gear sets 2 , 3 identical diameters.

[0022] As from Fig. As can be seen from 1, the second element 7 of the second planetary gear set3 , that is, the planet carrier, with the drive shaft 10 and the third element 8 of the first planetary gear set 2 , i.e., the ring gear, via a first hollow shaft 15 Permanently and rotationally fixed connection. The rotationally fixed connection of the planet carrier. 7 to the drive shaft 10 In this embodiment, this occurs at an axial height between the second planetary gear set. 3 and the gearbox output 14 .

[0023] Furthermore, the gearbox includes 1 a second hollow shaft 16 and an output shaft 17 The second hollow shaft 16 extends axially along both planetary gear sets 2 , 3 and is provided radially outside this. With the second hollow shaft 16 is the planet carrier 6 of the first planetary gear set 2 on the gearbox input 13facing side of the wheelset 2 The output shaft is permanently and rotationally fixed. 17 It is designed as a hollow shaft and forms the output shaft. 11 out and is radially outside the drive shaft 10 at the axial height of the power take-off shaft 12 provided. Between the second hollow shaft 16 and the output shaft 17 is a first switching element K1 It is designed as a coupling. The coupling K1 is in the axial direction between the second planetary gear set 3 and the downforce 11 designed and permanently rotationally fixed to the output shaft 17 and thus the downforce 11 as well as the second hollow shaft 16 connected. By actuating the clutch K1 can the second hollow shaft 16 and thus the planetary carrier 6 of the first planetary gear set 2 rotationally fixed to the output shaft 17 and thus the downforce 11be connected.

[0024] The gearbox 1 It also includes a third hollow shaft 18 , which are in the axial direction between the second planetary gear set 3 and the downforce 11 and in the radial direction between the drive shaft 10 and the second hollow shaft 16 is planned. The third hollow shaft 18 is permanently rotationally fixed to the ring gear 9 of the second planetary gear set 3 connected. In the power flow between the third hollow shaft 18 and the output shaft 17 is a second switching element K2 It is designed as a clutch. The second switching element is... K2 permanently rotationally fixed with the third element 9 of the second planetary gear set 3 and the output shaft 17 and thus the downforce 11 connected. By actuating the clutch K2 can the third hollow shaft 18and thus the hollow gear 9 of the second planetary gear set 3 rotationally fixed to the output shaft 17 and thus the downforce 11 be connected.

[0025] The gearbox 1 It also includes a fourth hollow shaft 19 , which extend axially along both planetary gear sets 2 , 3 and furthermore in the direction of the gearbox input 13 extends as well as radially within the first 15 and second hollow shaft 16 is arranged on the third hollow shaft. 19 The sun wheel is at one end 5 of the second planetary gear set 3 It is mounted as a fixed gear. The third hollow shaft extends from this one end. 19 away from the second planetary gear set 3 towards the gearbox input 13 along the first planetary gear set 2 . In the present case, on the third hollow shaft 19 also the sun wheel4 of the first planetary gear set 2 attached as a fixed wheel.

[0026] Furthermore, the gearbox includes 1 a variator with a first energy converter 20 and a second energy converter 21 The energy converters 20 , 21 In this embodiment, they are designed as electrical machines that are coaxial to the drive shaft 10 are planned. The electrical machines 20 , 21 Each includes a rotor 22 , 23 and one on a gearbox housing 24 fixed stator 25 , 26 The rotor 22 the first electric machine 20 In the present embodiment, it is permanently rotationally fixed to the fourth hollow shaft 19 connected, with the axial connection in front of the first planetary gear set 2 This has been done. Furthermore, the rotor 23 the second electric machine21 permanently rotationally fixed to the second hollow shaft 16 connected. The connection is also made in the axial direction in front of the first planetary gear set. 2 The electrical machines are coupled to each other via an electrical connection not shown.

[0027] Fig. Figure 2 shows a schematic view of a gearbox. 1 according to a second embodiment of the present invention. The construction of the gearbox. 1 balances that Fig. 1 with the exceptions described below. In contrast to the transmission design from Fig. 1 is the third hollow shaft 18' in this second embodiment permanently rotationally fixed to the output shaft 17' and thus the downforce 11 connected. Furthermore, the fourth hollow shaft 19' only the sun wheel 4 of the first planetary gear set 2 as a fixed gear. The gearbox 1In this second embodiment, it further includes a fifth hollow shaft. 27' , which extend axially from the second planetary gear set 3 along the first planetary gear set 2 to the gearbox input 13 extends in the radial direction. The fifth hollow shaft is 27' within the fourth hollow shaft 19' arranged. The fifth hollow shaft 27' the sun wheel indicates 5 of the second planetary gear set 3 as a fixed gear. Between the fourth hollow shaft 19' and the fifth hollow shaft 27' In this embodiment, a second switching element is included. K2' provided, which is designed as a clutch. The second switching element K2' is in the axial direction in front of the variator and the first and second planetary gear sets 2 , 3 arranged. Furthermore, the second switching element K2' permanently rotationally fixed with the fourth hollow shaft 19'and the fifth hollow shaft 27' connected. By actuating the clutch K2' can the fourth hollow shaft 19' and thus the sun wheel 4 of the first planetary gear set 2 rotationally fixed to the fifth hollow shaft 27' and thus to the sun gear 5 of the second planetary gear set 3 be connected.

[0028] Fig. Figure 3 shows a shift pattern of the transmissions from Fig. 1-2. As from Fig. As can be seen in section 3, there are two driving areas. FB1 and FB2 be switched. In the first driving range FB1 will the clutch K1 of the gearbox 1 activated, so that the second element 6 of the first planetary gear set 2 with the downforce 11 via the second hollow shaft 16 and the output shaft 17 It is connected in a rotationally fixed manner. The second coupling K2 / K2' It is not activated. This provides an output-coupled system. In the second driving range FB2 Only the clutch will be replaced K2 / K2' activated. Thus, in the Fig. In the embodiment shown in 1, the third element 9 of the second planetary gear set 3 rotationally fixed to the output 11 via the third hollow shaft 18 and the output shaft 17 connected. In the Fig. In the embodiment shown in 2, the sun gears 4 , 5 of the first and second planetary gear set 2 , 3 via the fourth and fifth hollow shaft 19' , 27' They are connected to each other in a rotationally fixed manner. This allows for the provision of a compound-coupled system. By providing the two travel ranges FB1 and FB2 can the gear ratio 1 will be increased.

[0029] The in Fig. 1-2 gearboxes shown 1 They can also be expanded to include a reversing unit / reversing gearbox. The reversing unit allows the driving ranges to be adjusted. FB1 and FB2 both forward and reverse travel are provided. The following describes possible configurations of the turning group in conjunction with the one in Fig. The embodiment shown in 1 is described, wherein the turning groups are also equipped with the one shown in Fig. 2 can be combined in the embodiment shown.

[0030] Fig. Figure 4 shows a turning group connected on the output side. 30 , which is connected to the output shaft 17 and thus the downforce 11 , who in Fig. 1-2 gearboxes shown 1 is permanently and rotationally fixed. The turning group 30 is behind the switching elements in the axial direction K1 , K2 provided for and includes an output wave 31 , which run parallel to the drive shaft10 and radially outside the energy converter 20 , 21 is planned. The turning group 30 also includes a first W1 and a second coupling W2 , which are coaxial to the drive shaft 10 are provided for. Both positive-locking couplings, e.g., jaw couplings, and friction-locking couplings, e.g., multi-plate couplings, are conceivable here. By actuating the first coupling W1 will the output shaft 17 via a spur gear stage with the output shaft 31 the turning group 30 connected. The spur gear stage includes one on the output shaft. 31 intended fixed wheel 32 and a loose wheel combing with it 33 , which is via the first clutch W1 with the output shaft 17 It can be connected in a rotationally fixed manner. By actuating the second coupling W2 will the output shaft 17 via another spur gear stage with the output shaft31 mechanically interconnected. The further spur gear stage comprises one on the output shaft. 31 intended fixed wheel 34 , which has an intermediate gear 35 combs, which in turn is equipped with a loose wheel 36 combs. The loose wheel 36 can be achieved by actuating the clutch W2 with the output shaft 17 They must be connected in a rotationally fixed manner. The actuation of the first coupling W1 This therefore results in a direction of rotation of the output shaft 31 , which are opposite to the direction of rotation when the second clutch is engaged W2 is.

[0031] Fig. 5 and Fig. Figure 6 shows further embodiments of the present invention. In these embodiments, a turning group is 40 or 50 provided on the drive side and in the axial direction in front of the variator and the planetary gear sets 2 , 3 arranged. The in Fig. The embodiment shown in Figure 5 comprises a minus planetary gear set. 41 , whose sun wheel 42 on the drive shaft 10 is designed as a fixed gear. The planet carrier 43 is via a switching element designed as a brake B40 on a case 44 lockable. Furthermore, the ring gear 45 of the planetary gear set 41 via a switching element designed as a clutch K40 rotationally fixed to the drive shaft 10 and thus the sun wheel 42 be connected. The in Fig. The embodiment shown in section 6 includes a plus planetary gear set. 51 , whose sun wheel 52 on the drive shaft 10 is designed as a fixed gear. The hollow gear 53 of the planetary gear set 51 is via a switching element B50 , which is designed as a brake, on a housing 54 Determinable. The planetary carrier 55It carries at least one meshing planetary gear pair, one of the planetary gears being connected to the radially surrounding ring gear. 53 and the other one with the radially inward sun wheel 52 combs. Furthermore, the planetary carrier 55 via a switching element designed as a clutch K50 with the sun wheel 52 Can be connected in a rotationally fixed manner. In the in Fig. 5 and Fig. In the embodiments shown in 6, the first hollow shaft 15" not permanently rotationally fixed to the drive shaft 10 , but permanently rotationally fixed to the ring gear 45 ( Fig. 5) or the planetary carrier 55 ( Fig. 6) connected. The first hollow shaft indicates this. 15" such a design that it is independent of the second element 7 of the second planetary gear set 3 radially within the first and second planetary gear set 2 , 3 to the gearbox input 13up to the turning point 40 , 50 that runs. By blocking the in Fig. 5 and Fig. 6 planetary gear set shown 41 , 51 by actuating the clutch K40 , K50 can a first direction of rotation of the first hollow shaft 15" This can be achieved by reversing the direction of rotation of the first hollow shaft. 15" can be achieved by fixing the planetary carrier 43 or the ring gear 53 by applying the brake B40 , B50 to be realized.

[0032] Fig. Figure 7 shows another embodiment of the gearbox. 1 of the present invention. The in Fig. The embodiment shown in 7 is an alternative embodiment of the one described in Fig. 4 shown embodiment with the output-side reversing group 30 As from Fig. As can be seen in section 7, the energy converters 20"' , 21"' of the gearbox of the in Fig.In embodiments 1-6 shown, also parallel to the drive shaft. 10 be trained. Regarding energy converters 20"' , 21"' These could all be electrical machines. The electrical machines 20"' , 21"' can relate to each other in relation to the drive shaft 10 opposite each other. The electrical machines 20"' , 21"' each have a rotor shaft 61 and 62 on, which are parallel to the drive shaft 10 is arranged. With the respective rotor shaft 61 , 62 is a rotor 22"' , 23"' connected, which is relative to one on a housing 63 , 64 fixed stator 25"' , 26"' can rotate. The first energy converter 20"' In the present embodiment, the fourth hollow shaft is connected via a spur gear stage. 19"' connected. The spur gear stage includes a hollow shaft on the first hollow shaft. 19"'intended fixed wheel 65 , which has one on the rotor shaft 61 intended fixed wheel 66 combs. The second energy converter 21"' is connected to the second hollow shaft via a two-stage spur gear stage 16"' connected. The spur gear stage includes a gear mounted on the rotor shaft. 62 of the second energy converter 21"' intended fixed wheel 67 , which is on an intermediate shaft 68 intended fixed wheel 69 combs. On the intermediate shaft 68 is another fixed wheel 70 planned, which in turn is connected to a second hollow shaft 16"' intended fixed wheel 71 combs. Reference symbol list 1 Power-split continuously variable transmission 2, 3 first, second planetary gear set 4, 6, 8 first, second, third element first planetary gear set 5, 7, 9 first, second, third element second planetary gear set 10, 12 Drive, drive shaft, power take-off shaft 11 Drive 13, 14 Gearbox input, gearbox output 15, 15" first hollow shaft 16, 16"' second hollow shaft 17, 17', 31 Output shaft, Output shaft 18, 18' third hollow shaft 19, 19', 19"' fourth hollow shaft 20, 20"', 21, 21"' first, second energy converter 22, 22"', 23, 23"' Rotor first, second energy converter 24, 44, 54, 63, 64 cases 25, 25"', 26, 26"' Stator first, second energy converter 30, 40, 50 Turning group K1, K2, K2' clutch B40, B50 brake W1, W2, K40, K50 clutch FB1, FB2 driving areas 32, 34 Fixed wheel 33, 35, 36 Loose wheel, intermediate wheel 41, 51 Planetary gear set 42.52 sun wheel 43, 55 Planetary carriers 45, 53 ring gear 61, 62 Rotor shaft 65, 66 fixed wheel 67, 69, 70, 71 Fixed wheel 68 Intermediate shaft

Claims

[1] Power-split continuously variable transmission (1) with a drive (10), an output (11), a first and a second planetary gear set (2, 3), a variator with a first and a second energy converter (20; 20"', 21; 21"'), and a first and a second switching device (K1, K2; K2'); wherein the planet gear sets (2, 3) each comprise three elements, the first element of the respective planet gear set being formed by a sun gear (4, 5), the second element of the respective planet gear set being formed by a planet carrier (6, 7) in the case of a minus planet gear set and by a ring gear in the case of a plus planet gear set, and the third element of the respective planet gear set being formed by a ring gear (8, 9) in the case of a minus planet gear set and by a planet carrier in the case of a plus planet gear set; wherein the second element (7) of the second planetary gear set (3) is permanently rotationally fixed to the third element (8) of the first planetary gear set (2) and mechanically operatively connected to the drive (10), the first energy converter (20; 20'') is mechanically operatively connected to the first element (4) of the first planetary gear set (2) and the second energy converter (21; 21'') is mechanically operatively connected to the second element (6) of the first planetary gear set (2), and the second element (6) of the first planetary gear set (2) can be rotationally fixedly connected to the output (11) via the first switching device (K1) in order to provide a first transmission range (FB1); and wherein the first element (4) of the first planetary gear set (2) is connected to the first element (5) of the second planetary gear set (3) via a first connection and the third element (9) of the second planetary gear set (3) is connected to the output (11) via a second connection, wherein one of the first and second connections can be switched via the second switching device (K2; K2') to establish a rotationally fixed connection in order to provide a second transmission range (FB2), and the other of the first and second connections is designed as a permanently rotationally fixed connection. [2] Power-split continuously variable transmission (1) according to claim 1, characterized by , that the first connection via the second switching device (K2) can be switched to establish a rotationally fixed connection in order to provide the second transmission range (FB2), and the second connection is designed as a permanently rotationally fixed connection. [3] Power-split continuously variable transmission (1) according to claim 1, characterized by , that the second connection via the second switching device (K2') can be switched to establish a rotationally fixed connection in order to provide the second transmission range (FB2), and the first connection is designed as a permanently rotationally fixed connection. [4] Power-split continuously variable transmission (1)) according to one of the preceding claims, characterized by , that the second element (6) of the first planetary gear set (2) and the output (11) are permanently connected to the first switching device (K1) in a rotationally fixed manner. [5] Power-split continuously variable transmission (1) according to any one of the preceding claims, characterized by , that the energy converters are designed as electrical machines (20, 21; 20'', 21''). [6] Power-split continuously variable transmission (1) according to any one of the preceding claims, characterized by, that at least one of the energy converters (20'') is connected to the first planetary gear set (2) via a pre-transmission (65, 66). [7] Power-split continuously variable transmission (1) according to any one of the preceding claims, characterized by , that at least one of the energy converters (20) is designed coaxially to the drive (10). [8] Power-split continuously variable transmission (1) according to any one of the preceding claims, characterized by , that at least one of the energy converters (20'') is designed parallel to the axis of the drive (10). [9] Power-split continuously variable transmission (1) according to one of the preceding claims, further comprising a reversing gear (30; 40; 50) for providing the first and second transmission range (FB1, FB2) in forward and reverse directions, wherein the reversing gear (30; 40; 50) is provided in the power flow through the transmission (1) before the drive (10) or after the output (11). [10] Power-split continuously variable transmission (1) according to any one of the preceding claims, characterized by , that the first and second planetary gear set (2, 3) are each designed as a minus planetary gear set. [11] Drive train for a working machine with a power-split continuously variable transmission (1) according to any one of claims 1 to 10. [12] Working machine with a drive train according to claim 11.

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